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Unlike the single-phase portion of the condenser, the two-phase section was solved by iterating over the quality of the ethanol from 1 to 0 in steps of 0.05. A similar series of equations as those outlined for the single-phase section were solved at each iteration, with the quality taken to be the average of the inlet and outlet qualities for each slice. Therefore, the length of each condenser slice was found and, along with the length of the single-phase section, were summed to arrive at the overall length. The two-phase representative point is the first quality step from a quality of 1.00 to a quality of 0.95 (Table 5-10). For this two-phase representative point, the hot side inlet temperature is 90.0°C, the cold side inlet temperature is 25°C, and the minimum heat capacity rate is 10.4 J s-1 K-1, giving a maximum heat transfer rate of 0.68 kW (equation (5.23)). The actual heat transfer rate is 0.60 kW, yielding a heat exchanger effectiveness of 87.4%. The relationship between effectiveness and NTUs of the two-phase section differs from that of the single-phase due to the large difference in heat capacity rates between the two-phase ethanol and air, resulting in a heat capacity ratio of essentially zero. The corresponding heat exchanger effectiveness/NTU relation becomes [49]: εtp 1exp(σTU) (5.54) The representative point for the two-phase slice of the condenser (for one quality step) has an effectiveness of 87.4% which yields an NTU of 2.07 and a total thermal resistance of 0.046 K W-1. The same thermal resistances described by equation (5.28) also exists in the two-phase section of the condenser. The two-phase ethanol flow required an appropriate heat transfer coefficient correlation based on the quality of the fluid. The Shah correlation was chosen because of the broad data set used to formulate the correlation, which included data using ethanol [53]. The correlation is represented by the following formulae: 97PDF Image | WASTE HEAT RECOVERY FROM A HIGH TEMPERATURE DIESEL ENGINE
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